US11318589B2 - Impact tool - Google Patents
Impact tool Download PDFInfo
- Publication number
- US11318589B2 US11318589B2 US16/278,382 US201916278382A US11318589B2 US 11318589 B2 US11318589 B2 US 11318589B2 US 201916278382 A US201916278382 A US 201916278382A US 11318589 B2 US11318589 B2 US 11318589B2
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- US
- United States
- Prior art keywords
- anvil
- hammer
- motor
- impact tool
- drive assembly
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
- B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
- B25B21/026—Impact clutches
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
- B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
- B25B23/02—Arrangements for handling screws or nuts
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D11/00—Portable percussive tools with electromotor or other motor drive
- B25D11/04—Portable percussive tools with electromotor or other motor drive in which the tool bit or anvil is hit by an impulse member
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D11/00—Portable percussive tools with electromotor or other motor drive
- B25D11/06—Means for driving the impulse member
- B25D11/066—Means for driving the impulse member using centrifugal or rotary impact elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
- B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
- B25B23/147—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for electrically operated wrenches or screwdrivers
- B25B23/1475—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for electrically operated wrenches or screwdrivers for impact wrenches or screwdrivers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
- B25D16/006—Mode changers; Mechanisms connected thereto
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
- B25D2216/0007—Details of percussion or rotation modes
- B25D2216/0023—Tools having a percussion-and-rotation mode
Definitions
- the present invention relates to power tools, and more specifically to impact tools.
- Impact tools or wrenches are typically utilized to provide a striking rotational force, or intermittent applications of torque, to a tool element or workpiece (e.g., a fastener) to either tighten or loosen the fastener.
- a tool element or workpiece e.g., a fastener
- impact wrenches are typically used to loosen or remove stuck fasteners (e.g., an automobile lug nut on an axle stud) that are otherwise not removable or very difficult to remove using hand tools.
- the present invention provides, in one aspect, an impact tool including a housing, an electric motor supported in the housing, and a drive assembly for converting a continuous torque input from the motor to consecutive rotational impacts upon a workpiece capable of developing at least 1,700 ft-lbs of fastening torque.
- the drive assembly includes an anvil rotatable about an axis and having a head adjacent a distal end of the anvil. The head has a minimum cross-sectional width of at least 1 inch in a plane oriented transverse to the axis.
- the drive assembly also includes a hammer that is both rotationally and axially movable relative to the anvil for imparting the consecutive rotational impacts upon the anvil, and a spring for biasing the hammer in an axial direction toward the anvil.
- the present invention provides, in another aspect, an impact tool including a housing and a brushless electric motor supported in the housing.
- the motor has a nominal diameter of at least 50 mm, a stator with a plurality of stator windings, and a rotor with a plurality of permanent magnets.
- the impact tool also includes a battery pack supported by the housing for providing power to the motor.
- the battery pack has a nominal voltage of at least 18 Volts and a nominal capacity of at least 5 Ah.
- the impact tool also includes a drive assembly for converting a continuous torque input from the motor to consecutive rotational impacts upon a workpiece capable of developing at least 1,700 ft-lbs of fastening torque without exceeding 100 amperes of current drawn by the motor.
- the drive assembly includes an anvil, a hammer that is both rotationally and axially movable relative to the anvil for imparting the consecutive rotational impacts upon the anvil, and a spring for biasing the hammer in an axial direction toward the anvil.
- the present invention provides, in another aspect, an impact tool including a housing and a brushless electric motor supported in the housing.
- the motor includes a stator with a plurality of stator windings and a rotor with a plurality of permanent magnets.
- the impact tool also includes a battery pack supported by the housing for providing power to the motor.
- the battery pack has a nominal voltage of at least 18 Volts and a nominal capacity of at least 5 Ah.
- the impact tool also includes a drive assembly for converting a continuous torque input from the motor to consecutive rotational impacts upon a workpiece.
- the drive assembly includes an anvil, a hammer that is both rotationally and axially movable relative to the anvil for imparting the consecutive rotational impacts upon the anvil at a rate of no more than 1 impact per revolution of the hammer to provide at least 90 Joules of impact energy to the anvil per revolution of the hammer, and a spring for biasing the hammer in an axial direction toward the anvil.
- FIG. 1 is a perspective view of an impact wrench according to one embodiment.
- FIG. 2 is a cross-sectional view of the impact wrench of FIG. 1 , taken along line 2 - 2 in FIG. 1 .
- FIG. 3 is a perspective cross-sectional view, illustrating a hammer and an anvil of the impact wrench of FIG. 1 .
- FIG. 4A is a perspective view of the anvil of FIG. 3 .
- FIG. 4B is another perspective view of the anvil of FIG. 3 .
- FIG. 4C is a front view of the anvil of FIG. 3 .
- FIG. 5A is a perspective view of an anvil according to another embodiment, usable with the impact wrench of FIG. 1 .
- FIG. 5B is a front view of the anvil of FIG. 5A .
- FIG. 6 is a cross-sectional view of a drive assembly according to one embodiment that may be used with the impact wrench of FIG. 1 .
- FIG. 7 is an exemplary graph illustrating an axial position of the hammer versus an angular position of the hammer during operation of the impact wrench of FIG. 1 in a first mode.
- FIG. 8 is an exemplary graph illustrating an axial position of the hammer versus an angular position of the hammer during operation of the impact wrench of FIG. 1 in a second mode.
- FIGS. 9A-E illustrate operation of the impact wrench of FIG. 1 in the second mode.
- FIG. 10 is a perspective view of an anvil according to another embodiment.
- FIG. 11 is another perspective view of the anvil of FIG. 14 .
- FIG. 12 is a perspective view of an impact wrench according to another embodiment.
- FIG. 13 is a cross-sectional view of the impact wrench of FIG. 12 .
- FIG. 14 is an enlarged cross-sectional view of a portion of the impact wrench of FIG. 12 .
- FIG. 1 illustrates a power tool in the form of an impact tool or impact wrench 10 .
- the impact wrench 10 includes a housing 14 with a motor housing portion 18 , a front housing portion 22 coupled to the motor housing portion 18 (e.g., by a plurality of fasteners), and a generally D-shaped handle portion 26 disposed rearward of the motor housing portion 18 .
- the handle portion 26 includes a grip 27 that can be grasped by a user operating the impact wrench 10 .
- the grip 27 is spaced from the motor housing portion 18 such that an aperture 28 is defined between the grip 27 and the motor housing portion 18 .
- the handle portion 26 and the motor housing portion 18 are defined by cooperating clamshell halves, and the front housing portion 22 is a unitary body.
- a rubber boot or end cap may cover a front end of the front housing portion 22 to provide protection for the front housing portion 22 .
- the rubber boot may be permanently affixed to the front housing portion 22 or removable and replaceable.
- the impact wrench 10 has a battery pack 34 removably coupled to a battery receptacle 38 located at a bottom end of the handle portion 26 (i.e. generally below the grip 27 ).
- the battery pack 34 includes a housing 39 enclosing a plurality of battery cells (not shown), which are electrically connected to provide the desired output (e.g., nominal voltage, current capacity, etc.) of the battery pack 34 .
- each battery cell has a nominal voltage between about 3 Volts (V) and about 5 V.
- the battery pack 34 preferably has a nominal capacity of at least 5 Amp-hours (Ah) (e.g., with two strings of five series-connected battery cells (a “5S2P” pack)).
- the battery pack 34 has a nominal capacity of at least 9 Ah (e.g., with three strings of five series-connected battery cells (a “5S3P pack”).
- the illustrated battery pack 34 has a nominal output voltage of at least 18 V.
- the battery pack 34 is rechargeable, and the cells may have a Lithium-based chemistry (e.g., Lithium, Lithium-ion, etc.) or any other suitable chemistry.
- an electric motor 42 supported within the motor housing portion 18 , receives power from the battery pack 34 ( FIG. 1 ) when the battery pack 34 is coupled to the battery receptacle 38 .
- the illustrated motor 42 is a brushless direct current (“BLDC”) motor with a stator 46 that has a plurality of stator windings 48 ( FIG. 2 ).
- a rotor or output shaft 50 of the motor 42 has a plurality of permanent magnets 52 .
- the motor 42 has a nominal diameter of at least 50 mm. In other embodiments, the motor 42 has a nominal diameter of at least 60 mm. In other embodiments, the motor 42 has a nominal diameter of at least 70 mm.
- the stator 46 has a stack length of at least 18 mm. In some embodiments, the stator 46 has a stack length of at least 22 mm. In some embodiments, the stator 46 has a stack length of at least 30 mm. In some embodiments, the stator 46 has a stack length of at least 35 mm.
- the motor 42 is a BL60-18 motor having a nominal diameter of 60 mm and a stack length of 18 mm. In another embodiment, the motor 42 is a BL60-30 motor having a nominal diameter of 60 mm and a stack length of 30 mm. In another embodiment, the motor 42 is a BL70-35 motor having a nominal diameter of 70 mm and a stack length of 35 mm.
- Table 1 lists an approximate peak power and efficiency of each of these exemplary motors 42 when paired with a battery pack 34 having a particular capacity. It should be understood that the peak power and efficiency for each of the motors listed in Table 1 may vary (e.g., due to manufacturing and assembly tolerances).
- the output shaft 50 is rotatable about an axis 54 relative to the stator 46 .
- a fan 58 is coupled to the output shaft 50 (e.g., via a splined connection) adjacent a front end of the motor 42 .
- the impact wrench 10 also includes a trigger 62 provided on the handle portion 26 that selectively electrically connects the motor 42 and the battery pack 34 to provide DC power to the motor 42 .
- a solid state switch 64 carries substantially all of the current from the battery pack 34 to the motor 42 .
- the solid state switch 64 is disposed within the grip 27 , generally below the trigger 62 .
- the impact wrench 10 may include a power cord for electrically connecting the motor 42 to a source of AC power.
- the impact wrench 10 may be configured to operate using a different power source (e.g., a pneumatic power source, etc.).
- the battery pack 34 is the preferred means for powering the impact wrench 10 , however, because a cordless impact wrench advantageously requires less maintenance (e.g., no oiling of air lines or compressor motor) and can be used in locations where compressed air or other power sources are unavailable.
- the impact wrench 10 further includes a gear assembly 66 coupled to the motor output shaft 50 and a drive assembly 70 coupled to an output of the gear assembly 66 .
- the gear assembly 66 is supported within the housing 14 by a gear support 74 , which is coupled between the motor housing portion 18 and the front housing portion 22 in the illustrated embodiment.
- the gear support 74 and the front housing portion 22 collectively define a gear case.
- the gear assembly 66 may be configured in any of a number of different ways to provide a speed reduction between the output shaft 50 and an input of the drive assembly 70 .
- the illustrated gear assembly 66 includes a helical pinion 82 formed on the motor output shaft 50 , a plurality of helical planet gears 86 meshed with the helical pinion 82 , and a helical ring gear 90 meshed with the planet gears 86 and rotationally fixed within the gear case (e.g., via splines formed in the front housing portion 22 or any other suitable arrangement).
- the planet gears 86 are mounted on a camshaft 94 of the drive assembly 70 such that the camshaft 94 acts as a planet carrier. Accordingly, rotation of the output shaft 50 rotates the planet gears 86 , which then advance along the inner circumference of the ring gear 90 and thereby rotate the camshaft 94 .
- the gear assembly 66 provides a gear ratio from the output shaft 50 to the camshaft 94 between 10:1 and 14:1; however, the gear assembly 66 may be configured to provide other gear ratios.
- the drive assembly 70 includes an anvil 200 , extending from the front housing portion 22 , to which a tool element (e.g., a socket; not shown) can be coupled for performing work on a workpiece (e.g., a fastener).
- the drive assembly 70 is configured to convert the continuous rotational force or torque provided by the motor 42 and gear assembly 66 to a striking rotational force or intermittent applications of torque to the anvil 200 when the reaction torque on the anvil 200 (e.g., due to engagement between the tool element and a fastener being worked upon) exceeds a certain threshold.
- the drive assembly 66 includes the camshaft 94 , a hammer 204 supported on and axially slidable relative to the camshaft 94 , and the anvil 200 .
- the drive assembly 70 further includes a spring 208 biasing the hammer 204 toward the front of the impact wrench 10 (i.e., in the right direction of FIG. 3 ).
- the spring 208 biases the hammer 204 in an axial direction toward the anvil 200 , along the axis 54 .
- a thrust bearing 212 and a thrust washer 216 are positioned between the spring 208 and the hammer 204 .
- the thrust bearing 212 and the thrust washer 216 allow for the spring 208 and the camshaft 94 to continue to rotate relative to the hammer 204 after each impact strike when lugs 218 on the hammer 204 ( FIG. 3 ) engage with corresponding anvil lugs 220 .
- the camshaft 94 further includes cam grooves 224 ( FIG. 2 ) in which corresponding cam balls 228 are received.
- the cam balls 228 are in driving engagement with the hammer 204 and movement of the cam balls 228 within the cam grooves 221 allows for relative axial movement of the hammer 204 along the camshaft 94 when the hammer lugs 218 and the anvil lugs 220 are engaged and the camshaft 94 continues to rotate.
- a bushing 222 is disposed within the front portion 22 of the housing to rotationally support the anvil 200 .
- a washer 226 which in some embodiments may be an integral flange portion of bushing 222 , is located between the anvil 200 and a front end of the front housing portion 22 . In some embodiments, multiple washers 226 may be provided as a washer stack.
- the illustrated anvil 200 includes a head 232 at its distal end.
- the head 232 has a generally square cross-sectional shape in a plane oriented transverse a rotational axis of the anvil 200 (i.e. the axis 54 ).
- the illustrated head 232 has a minimum cross-sectional width 236 of about 1-inch (i.e. a nominal width of 1-inch), such that head 232 can be connected to standard, 1-inch square drive fasteners and tool elements.
- a circle 237 circumscribing the head 236 has a diameter 239 of about 1.22 inches.
- the head 232 may have other nominal widths (e.g., 1 ⁇ 2 inch, 3 ⁇ 4 inch, 11 ⁇ 2 inch, etc.).
- the head 232 may include other geometries (e.g., hexagonal, spline patterns, and the like).
- Each of the illustrated anvil lugs 220 defines a base or cord dimension 240 ( FIG. 4A ) and a nominal contact area 244 ( FIG. 4B ) where the hammer lugs 218 contact the anvil lug 220 .
- the base dimension 240 is at least 14 mm
- the nominal contact area 244 is at least 260 mm 2 .
- the base dimension 240 and the nominal contact area 244 are larger than that of typical impact wrench anvils in order to provide greater strength and higher torque transfer through the anvil 200 .
- the anvil 200 may be interchangeable with anvils of various lengths and/or head sizes.
- the illustrated anvil 200 is relatively long and may advantageously provide the impact wrench 10 with longer reach.
- FIGS. 5A and 5B illustrate an anvil 200 a according to another embodiment.
- the anvil 200 a is shorter in length than the anvil 200 . Accordingly, the anvil 200 a may be used when a more compact length is desired for the impact wrench 10 , or to reduce the weight of the impact wrench 10 .
- the anvil 200 a includes a head 232 a with a plurality of axially-extending splines 233 a that collectively define a spline pattern ( FIG. 5A ).
- the illustrated spline pattern is an ASME No. 5 spline pattern, with a cross-sectional width 236 a of about 1.615 inches (corresponding to a nominal size of 15 ⁇ 8 inches).
- the head 232 a can be connected to standard, ASME No. 5 spline drive fasteners and tool elements.
- a circle 237 a circumscribing the head 236 a has a diameter 239 a that is equal to the cross-sectional width 236 a.
- the anvil 200 a includes anvil lugs 220 a , each defining a base or cord dimension 240 a and a nominal contact area 244 a where the hammer lugs 218 contact the anvil lug 220 a .
- the base dimension 240 a may be at least 23 mm
- the contact area 244 a may be at least 335 mm 2 .
- the impact wrench 10 may have an anvil 200 , 200 a with a head 232 , 232 a having a cross-sectional width of at least 1-inch. This relatively large head size may be used for high-torque fastening tasks beyond of the capabilities of typical battery-powered impact tools.
- the illustrated impact wrench 10 further includes a second handle 150 coupled to a second handle mount 154 .
- the second handle 150 is a generally U-shaped handle with a central grip portion 156 , which may be covered by an elastomeric overmold.
- the second handle mount 154 includes a band clamp 158 that surrounds the front housing portion 22 .
- the second handle mount 154 also includes an adjustment mechanism 162 .
- the adjustment mechanism 162 can be loosened to permit adjustment of the second handle 150 .
- the second handle 150 is rotatable about an axis 170 when the adjustment mechanism 162 is loosened.
- loosening the adjustment mechanism 162 may also loosen the band clamp 158 to permit rotation of the second handle 150 and the second handle mount 154 about the axis 54 ( FIG. 2 ).
- an operator depresses the trigger 62 to activate the motor 42 , which continuously drives the gear assembly 66 and the camshaft 94 via the output shaft 50 .
- the cam balls 228 drive the hammer 204 to co-rotate with the camshaft 94 , and the hammer lugs 218 engage, respectively, driven surfaces of the anvil lugs 220 to provide an impact and to rotatably drive the anvil 200 and the tool element.
- the hammer 204 moves or slides rearward along the camshaft 94 , away from the anvil 200 , so that the hammer lugs disengage the anvil lugs 220 .
- the cam balls 228 situated in the respective cam grooves 224 in the camshaft 94 move rearward in the cam grooves 224 .
- the spring 208 stores some of the rearward energy of the hammer 204 to provide a return mechanism for the hammer 204 .
- the hammer 204 continues to rotate and moves or slides forwardly, toward the anvil 200 , as the spring 208 releases its stored energy, until the drive surfaces of the hammer lugs 218 re-engage the driven surfaces of the anvil lugs 220 to cause another impact.
- the impact wrench 10 may be operable in a first mode to deliver two blows or impacts to the anvil 200 per revolution of the camshaft 94 and additionally or alternatively in a second mode to deliver a single blow or impact to the anvil 200 per revolution of the camshaft 94 .
- Components of the impact wrench 10 e.g., the spring 208 , the camshaft 94 , and/or the hammer 204 ) may be replaced or modified to operate the impact wrench 10 in either the first mode or the second mode.
- FIG. 6 illustrates a drive assembly 70 ′ that may replace the drive assembly 70 to configure the impact wrench 10 for operating in the second mode.
- the drive assembly 70 ′ includes a camshaft 94 ′ with cam grooves 224 ′ and cam ball 228 ′, a hammer 204 ′, and a spring 208 ′ that may differ in a variety of ways from the components of the drive assembly 70 .
- the camshaft 94 ′ of the assembly 70 ′ is longer than the camshaft 94
- the cam grooves 224 ′ permit greater axial displacement the hammer 204 ′.
- the spring 208 ′ is softer to accommodate greater compression due to the increased axial displacement of the hammer 204 ′.
- the hammer 204 ′ is axially displaceable in one direction along the camshaft 94 ′ by a distance of at least 40 millimeters.
- Table 2 provides a comparison between various aspects of the drive assembly 70 , which can be used to operate the impact wrench 10 in the first mode, and the drive assembly 70 ′, which can be used to operate the impact wrench 10 in the second mode.
- the drive assembly 70 ′ can also be used to operate the impact wrench 10 in the first mode when the motor 42 is operated at a lower speed, as discussed in greater detail below.
- FIG. 7 is an exemplary graph 250 illustrating operation of the impact wrench 10 in the first mode (i.e. two impacts per revolution).
- the graph 250 includes a curve 254 representing an axial position of the hammer 204 along the camshaft 94 versus a rotational position of the hammer 204 .
- the curve 254 includes a plurality of peaks 258 , each representing the rearmost position of the hammer 204 on the camshaft 94 .
- a period 262 of the curve 254 is defined between adjacent peaks 258 .
- An area A 1 under the curve 254 is proportional to the kinetic energy of the hammer 204 when it impacts the anvil 200 .
- FIG. 8 is an exemplary graph 250 ′ illustrating operation of the impact wrench 10 in the second mode (i.e. one impact per revolution).
- the graph 250 ′ includes a curve 254 ′ representing an axial position of the hammer 204 ′ along the camshaft 94 ′ versus a rotational position of the hammer 204 ′.
- the curve 254 ′ includes a plurality of peaks 258 ′, each representing the rearmost position of the hammer 204 ′ on the camshaft 94 ′.
- a period 262 ′ of the curve 254 ′ is defined between adjacent peaks 258 ′.
- An area A 2 under the curve 254 ′ is proportional to the kinetic energy of the hammer 204 ′ when it impacts the anvil 200 .
- the hammer 204 ′ is displaced a greater axial distance than the hammer 204 before reaching their respective rearmost axial positions.
- the area A 2 is greater than the area A 1 , indicating that more kinetic energy is transferred to the anvil 200 per impact in the second mode than in the first mode.
- the period 262 ′ is greater than the period 262 , indicating that fewer impacts per minute are delivered in the second mode than in the first mode.
- FIGS. 9A-E illustrate operation of the impact wrench 10 in the second mode (i.e. delivering one impact per revolution).
- the hammer 204 ′ includes first and second hammer lugs 218 A′, 218 B′, and the anvil 200 includes first and second anvil lugs 220 A, 220 B.
- FIG. 9A illustrates the hammer 204 ′ just prior to the hammer lugs 218 A′, 218 B′ impacting the anvil lugs 220 A, 220 B.
- the hammer 204 ′ rotates in the direction of arrow 270 while moving toward the anvil 200 .
- the first hammer lug 218 A′ impacts the first anvil lug 220 A
- the second hammer lug 218 B′ impacts the second anvil lug 220 B, as shown in FIG. 9B .
- the hammer 204 ′ moves away from the anvil 200 along the camshaft 94 ′, and begins to rotate relative to the anvil 200 in the direction of arrow 270 once the hammer lugs 218 A′, 218 B′ are clear of the anvil lugs 220 A, 220 B ( FIG. 9C ).
- the motor 42 accelerates the hammer 204 ′, and the hammer 204 ′ completes approximately an entire rotation before impacting the anvil 200 again as shown in FIG. 9E .
- the precise amount of rotation of the hammer 204 ′ may vary due to rebound effects. In the illustrated embodiment, the hammer 204 ′ rotates between 345 degrees and 375 degrees between successive impacts. In addition, when operating in the second mode, the first hammer lug 218 A′ always impacts the first anvil lug 220 A, and the second hammer lug 218 B′ always impacts the second anvil lug 220 B.
- Table 3 includes experimental results illustrating the fastening torque that the impact wrench 10 is capable of applying to a fastener when operating in the first mode (i.e. delivering two impacts per revolution).
- fastening torque means torque applied to a fastener in a direction increasing tension (i.e. in a tightening direction).
- Table 3 lists the current drawn by the motor 42 and the peak fastening torque exerted on five different 11 ⁇ 2 inch bolts over the course of ten seconds.
- the motor 42 used in these tests was a BL60-30 motor having a nominal diameter of 60 mm and a stator stack length of 30 mm.
- the drive assembly 70 of the impact wrench 10 converts the continuous torque input from the motor 52 to deliver consecutive rotational impacts on a workpiece, producing at least 1,700 ft-lbs of fastening torque without exceeding 100 A of current drawn by the motor 42 .
- the drive assembly 70 delivers consecutive rotational impacts on a workpiece, producing at least 1,700 ft-lbs of fastening torque without exceeding 80 A of current drawn by the motor 42 .
- the drive assembly 70 delivers consecutive rotational impacts on a workpiece, producing at least 1,800 ft-lbs of fastening torque without exceeding 100 A of current drawn by the motor 42 . In some embodiments, the drive assembly 70 delivers consecutive rotational impacts on a workpiece, producing at least 1,800 ft-lbs of fastening torque without exceeding 80 A of current drawn by the motor 42 .
- the drive assembly 70 delivers consecutive rotational impacts on a workpiece, producing at least 1,900 ft-lbs of fastening torque without exceeding 100 A of current drawn by the motor 42 . In some embodiments, the drive assembly 70 delivers consecutive rotational impacts on a workpiece, producing at least 1,900 ft-lbs of fastening torque without exceeding 80 A of current drawn by the motor 42 .
- the drive assembly 70 delivers consecutive rotational impacts on a workpiece, producing at least 2,000 ft-lbs of fastening torque without exceeding 100 A of current drawn by the motor 42 . In some embodiments, the drive assembly 70 delivers consecutive rotational impacts on a workpiece, producing at least 2,000 ft-lbs of fastening torque without exceeding 80 A of current drawn by the motor 42 .
- the impact wrench 10 can operate at a plurality of different speed settings.
- the operating mode of the impact wrench 10 i.e. the first mode or the second mode
- the drive assembly 70 ′ enables the impact wrench 10 to operate in the second mode when the motor 42 drives the output shaft 50 at a maximum speed and in the first mode when the motor 42 drives the output shaft 50 at a lower speed (e.g., about 60% of the maximum speed).
- a user may toggle between the first mode and the second mode by varying the operating speed of the motor 42 .
- Table 4 includes simulated performance data for the impact wrench 10 operating in the first mode and in the second mode at the maximum (100%) speed setting.
- the performance data was simulated for both a BL60-30 motor and a BL70-35 motor.
- the last column of Table 4 includes simulated performance data for the impact wrench 10 operating in the first mode at a lower (60%) speed setting.
- the hammer 204 ′ of the drive assembly 70 ′ is capable of providing at least 90 J of kinetic energy at impact, or “impact energy” per revolution of the hammer 204 ′ when operating in the second mode.
- the hammer 204 ′ is capable of providing at least 90 J of impact energy per revolution of the hammer 204 ′ without exceeding 100 A of current drawn by the motor 42 .
- the impact energy of the hammer 204 ′ in the second mode is significantly greater than the impact energy of the hammer 204 in the first mode.
- Table 4 illustrates that the motor 42 may draw less current in the second mode than in the first mode (e.g., approximately 30% less in some embodiments). The second mode may thus be particularly advantageous to overcome static friction when breaking loose stuck fasteners.
- Table 5 lists the mass (in kg) and mass-moment of inertia (in kg-m 2 ) for various components of the drive assemblies 70 and 70 ′.
- the anvil 200 may be interchangeable with anvils of various lengths and/or head sizes.
- FIGS. 10 and 11 illustrate an anvil 200 b according to another embodiment.
- the anvil 200 b is shorter in length than the anvil 200 . Accordingly, the anvil 200 b may be used when a more compact length is desired for the impact wrench 10 , or to reduce the weight of the impact wrench 10 .
- the anvil 200 b includes a head 232 b defining a nominal width 236 b . In some embodiments, the nominal width 236 b is 1 inch. In other embodiments, the anvil 200 b has a nominal width 236 b of 3 ⁇ 4 inch or 1 ⁇ 2 inch. As such, the anvil 200 b may be configured to accept standard 3 ⁇ 4 inch square drive tools elements or 1 ⁇ 2 inch square drive tool elements, respectively.
- the anvil 200 b includes anvil lugs 220 b , each defining a base or cord dimension 240 b and a nominal contact area 244 b where the hammer lugs 218 contact the anvil lug 220 b .
- the base dimension 240 b may be at least 11 mm
- the contact area 244 may be at least 190 mm 2 .
- the base dimension 240 may be at least 11 mm
- the contact area 244 may be at least 150 mm 2 .
- FIGS. 12-14 illustrate an impact wrench 310 according to another embodiment.
- the impact wrench 310 is similar to the impact wrench 10 described above, and the following description focuses only on the differences between the impact wrench 310 and the impact wrench 10 .
- features and elements of the impact wrench 310 corresponding with features and elements of the impact wrench 10 are given like references numbers plus ‘300.’
- features and elements of the impact wrench 310 may be incorporated into the impact wrench 10 , and vice versa.
- the impact wrench 310 has a generally T-shaped configuration that provides a reduced overall tool length compared to the impact wrench 10 of FIG. 1 .
- the impact wrench 310 includes a housing 314 with a motor housing portion 318 , a front housing portion 322 coupled to the motor housing portion 318 (e.g., by a plurality of fasteners), and a handle portion 326 extending downward from the motor housing portion 318 .
- the handle portion 326 includes a grip 327 that can be grasped by a user operating the impact wrench 310 .
- the handle portion 326 is positioned such that the camshaft 394 at least partially overlaps the handle portion 326 in a vertical direction (with reference to the orientation of FIG. 13 ).
- an axis 331 oriented transverse to a rotational axis 354 of the camshaft 394 passes through the handle portion 326 and intersects the camshaft 394 .
- the axis 331 also passes through the battery receptacle 334 .
- the output shaft 350 is rotatably supported by a first or forward bearing 398 and a second or rear bearing 402 ( FIG. 14 ).
- the helical gears 382 , 386 , 390 of the gear assembly 366 ( FIG. 13 ) advantageously provide higher torque capacity and quieter operation than spur gears, for example, but the helical engagement between the pinion 382 and the planet gears 386 produces an axial thrust load on the output shaft 350 .
- the impact wrench 310 includes a bearing retainer 406 that secures the rear bearing 402 both axially (i.e. against forces transmitted along the axis 354 ) and radially (i.e. against forces transmitted in a radial direction of the output shaft 350 ).
- the illustrated bearing retainer 406 includes a recess 410 formed adjacent a rear end of the motor housing portion 318 .
- An outer race 418 of the rear bearing 402 is received within the recess 410 , which axially and radially secures the outer race 418 to the motor housing portion 318 .
- An inner race 422 of the rear bearing 402 is coupled to the output shaft 350 (e.g., via a press-fit).
- the inner race 422 is disposed between a shoulder 426 on the output shaft 350 and a snap ring 430 coupled to the output shaft 350 opposite the shoulder 426 .
- the shoulder 426 and the snap ring 430 engage the inner race 422 to axially secure the inner race 422 to the output shaft 350 .
- the inner race 422 may be omitted, and the output shaft 350 may have a journaled portion acting as the inner race 422 .
- the helical engagement between the pinion 382 and the planet gears 386 produces a thrust load along the axis 354 of the output shaft 350 , which is transmitted to the rear bearing 402 .
- the bearing 402 is secured against this thrust load by the bearing retainer 406 .
Abstract
Description
TABLE 1 | |||||
Motor | BL60-18 | BL60-30 | BL70-35 | ||
Battery Capacity (Ah) | 5 | 9 | 12 | ||
Peak Power (W) | 948.6 | 1410.4 | 1784.4 | ||
Peak Efficiency | 80.7% | 84.3% | 85% | ||
TABLE 2 | |||
| Drive | ||
Assembly | |||
70 | |
||
Impacts per |
2 | 1 |
Spring Preload (N) | 860 | 350 |
Spring Rate (N/mm) | 65 | 32 |
Spring Preload Length (mm) | 78.93 | 78.93 |
Spring Wire Diameter (mm) | 6.19 | 6.19 |
Spring Mean Diameter (mm) | 47.72 | 47.72 |
Cam Shaft Diameter (mm) | 36 | 36 |
Cam Angle (deg) | 31.2 | 31.2 |
Cam Ball Diameter (mm) | 9.525 | 9.525 |
Hammer Mass (kg) | 1.42 | 1.42 |
Hammer Moment of Inertia (kg-m2) | 1.41E−03 | 1.41E−03 |
Hammer Axial Travel (mm) | 23.80 | 48.20 |
Gear Ratio | 11.4 | 11.4 |
TABLE 3 | ||||||
Bolt 1 | |
Bolt 3 | |
|
||
Current (A) | 78.11 | 78.7 | 79.32 | 77.12 | 77.41 |
Peak Fastening | 2382 | 1982 | 2162 | 2275 | 1877 |
Torque (ft-lbs) | |||||
TABLE 4 | ||||||
First | Second | First | Second | First | ||
Mode | Mode | Mode | Mode | | ||
Drive Assembly |
70 | 70′ | 70 | 70′ | 70′ | |
Motor Speed | 100% | 100% | 100% | 100% | 60% |
Impacts per |
2 | 1 | 2 | 1 | 2 |
Motor | BL60-30 | BL60-30 | BL70-35 | BL70-35 | BL70-35 |
Battery Capacity (Ah) | 9 | 9 | 9 | 9 | 9 |
Impacts per Minute | 2134 | 1247 | 1780 | 1082 | 612 |
Kinetic Energy at Impact (J) | 33.72 | 45.26 | 67.47 | 96.35 | 23.12 |
Developed Energy over 10 sec (J) | 11,993 | 9,407 | 20,016 | 17,375 | 2,358 |
Estimated Motor Current (A) | 67-83 | 51-64 | 138-172 | 75-94 | 76-95 |
TABLE 5 | |||
Moment of Inertia (kg-m2) | Mass (kg) | ||
|
4.73E−04 | 0.739 | ||
|
1.41E−03 | 1.423 | ||
|
5.54E−05 | 0.346 | ||
|
5.40E−04 | 1.762 | ||
|
1.30E−08 | 0.002 | ||
|
4.10E−08 | 0.004 | ||
|
2.65E−04 | 1.753 | ||
|
8.37E−05 | 0.536 | ||
TABLE 6 | |||
Nominal Head Size (in) | ½ | ½ | ¾ |
Motor Speed | 100% | 100% | 100% |
Impacts per |
2 | 2 | 2 |
Motor | BL60-22 | BL60-18 | BL60-18 |
Impacts per Minute | 2369 | 2246 | 2267 |
Kinetic Energy at Impact (J) | 18.45 | 25.72 | 26.36 |
Developed Energy over 10 sec (J) | 7285 | 9628 | 9960 |
Spring Preload (N) | 340 | 520 | 520 |
Spring Rate (N/mm) | 55 | 65 | 65 |
Spring Preload Length (mm) | 49.15 | 49.00 | 49.00 |
Spring Wire Diameter (mm) | 6.00 | 6.19 | 6.19 |
Spring Mean Diameter (mm) | 42.80 | 43.42 | 43.42 |
Cam Shaft Diameter (mm) | 20 | 21 | 21 |
Cam Angle (deg) | 30.5 | 31.2 | 31.2 |
Cam Ball Diameter (mm) | 6.35 | 6.60 | 6.60 |
Hammer Mass (kg) | 0.414 | 0.530 | 0.530 |
Hammer Moment of Inertia (kg-m2) | 2.44E−04 | 3.39E−04 | 3.39E−04 |
Gear Ratio | 11.4 | 12.0 | 11.4 |
Claims (20)
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US16/278,382 US11318589B2 (en) | 2018-02-19 | 2019-02-18 | Impact tool |
US17/734,691 US11964368B2 (en) | 2022-05-02 | Impact tool |
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US201862631986P | 2018-02-19 | 2018-02-19 | |
US16/278,382 US11318589B2 (en) | 2018-02-19 | 2019-02-18 | Impact tool |
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US17/734,691 Continuation US11964368B2 (en) | 2022-05-02 | Impact tool |
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US20190255687A1 US20190255687A1 (en) | 2019-08-22 |
US11318589B2 true US11318589B2 (en) | 2022-05-03 |
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US (1) | US11318589B2 (en) |
EP (1) | EP3755502A4 (en) |
CN (1) | CN213319858U (en) |
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Also Published As
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US20190255687A1 (en) | 2019-08-22 |
EP3755502A1 (en) | 2020-12-30 |
AU2019221782A1 (en) | 2020-10-08 |
US20220250216A1 (en) | 2022-08-11 |
WO2019161326A1 (en) | 2019-08-22 |
CN213319858U (en) | 2021-06-01 |
EP3755502A4 (en) | 2021-11-17 |
TWM582890U (en) | 2019-09-01 |
AU2019101751A4 (en) | 2020-11-05 |
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